CN112888879A

CN112888879A - Cylindrical gear differential mechanism

Info

Publication number: CN112888879A
Application number: CN201980069499.2A
Authority: CN
Inventors: T·霍夫曼
Original assignee: Desi Vogel Molding Technology Co ltd
Current assignee: Desi Vogel Molding Technology Co ltd
Priority date: 2018-10-24
Filing date: 2019-10-15
Publication date: 2021-06-01
Anticipated expiration: 2039-10-15
Also published as: US11365794B2; CN112888879B; WO2020083707A1; US20210356025A1; DE102018126551B3; EP3850244A1; KR20210099557A

Abstract

The invention relates to a spur gear differential (1), in particular for a motor vehicle, having a planet carrier (2) which is provided for rotation about a differential axis (X), a first output spur gear (3) which is arranged coaxially with respect to the differential axis (X), a second output spur gear (4) which is also arranged coaxially with respect to the differential axis (X), at least one pair (5) of intermeshing planet gears (6,7) which are rotatably arranged in the planet carrier (2), wherein the planet gears (6,7) each mesh with one output spur gear (3, 4). At least one of the output cylindrical gears (3,4) and/or the planet gears (6,7) has a conical toothing in such a way that, when the planet gears (6,7) rotate relative to one another, the at least one of the output cylindrical gears (3,4) and/or the planet gears (6,7) is moved into a position which causes a blocking effect. The invention also relates to a corresponding method for producing such a spur gear differential (1).

Description

Cylindrical gear differential mechanism

1. Field of the invention

The invention relates to a spur gear differential, in particular for a motor vehicle, having a planet carrier provided for rotation about a differential shaft, a first output spur gear arranged coaxially with the differential shaft, a second output spur gear also arranged coaxially with the differential shaft, and at least one pair of intermeshing planet gears rotatably arranged in the planet carrier, wherein the planet gears each mesh with one output spur gear. The invention also relates to a method for producing such a spur gear differential.

2. Background of the invention

Spur gear differentials of the type mentioned in the introduction are known in principle from the prior art. They are an alternative to the classical differentials, which work with bevel gear sets. In short, it should be achieved by means of a differential or a spur gear differential that the two wheels driven by the differential can rotate at different speeds, for example in order to achieve an overbending. Exemplary spur gear differentials are known from DE102012208806a1 and DE102007040475a 1.

Locking differentials are also known from the prior art, which are provided to counteract the effect caused by the differential by a locking effect. This may be advantageous in certain situations, for example, where a slip occurs on one of the wheels. That is, in this case, it would occur that in the case of a differential without a locking effect (open differential) one wheel rotates smoothly, while the other wheel does not rotate so much or even does not rotate. The locking effect now causes more torque to be transmitted to the non-slipping wheels, i.e. the relative speed between the output cylindrical gears is reduced. In some applications the blocking effect may even result in a rigid engagement between the output cylindrical gears, for example when the truck has to temporarily drive over difficult terrain or fields.

A disadvantage of the spur gear differentials known from the prior art is that they are relatively complicated to manufacture. This relates in particular to the tooth arrangement of the output spur and planetary gears. The aforementioned gears must therefore undergo several reworking steps (deburring, etc.) for functional normal use, in order in particular to be able to comply with the narrow tolerances required. Furthermore, spur gear differentials known from the prior art take up a relatively large amount of installation space, in particular if additional devices are to be used to achieve the locking effect of the spur gear differential.

In view of this prior art, the present invention provides the task of overcoming the above-mentioned disadvantages of the prior art, in particular of providing a spur gear differential which can be produced in a simple manner.

These and other tasks, which will be further mentioned or will be appreciated by the skilled person upon reading the following description, are accomplished by the subject matter and methods of the independent claims. Advantageous developments are the subject matter of the dependent claims to which they refer.

3. Detailed description of the invention

The cylindrical gear differential according to the present invention has: a planet gear carrier arranged for rotation about the differential shaft; a first output cylindrical gear coaxially arranged with respect to the differential shaft; a second output cylindrical gear also coaxially arranged with respect to the differential shaft; and at least one pair of intermeshing planet gears rotatably disposed in the planet carrier, wherein the planet gears are each in mesh with an output cylindrical gear. At least one (or all) of the output cylindrical gear and/or the planet gears have a conical toothing in such a way that, when the planet gears rotate relative to one another, at least one of the output cylindrical gear and/or the planet gears is moved into a position in which a blocking effect is produced.

The conical tooth structure here results in that a rotational movement can be converted into another movement by means of the oblique or conical shape of the tooth structure; thus, if two meshing gears rotate relative to each other, the gears move relative to each other in another direction, e.g. away from or towards each other (they are e.g. pushed away from each other by being subjected to a torque) because of the conical tooth structure of one or both of the gears. The additional movement of at least one of the output spur gear and/or the planetary gear is now advantageously used to create a blocking effect. The additional means for increasing the blocking effect can therefore be dispensed with in the best case or only a slight additional blocking effect needs to occur. Furthermore, the tapered tooth structure is suitable for more efficient manufacturing, since the manufacturing method suitable for tapered tooth structure manufacturing requires fewer reworking steps, and in the best case, the respective tooth structure can be formed in a single working step.

Preferably, the planet gears of the at least one pair of planet gears have conical teeth such that, when they rotate the planet gears relative to each other, the planet gears move towards the planet gear carrier into a position in which they press against the planet gear carrier and thus cause a blocking effect. Thus, the pressing of the planet gears against the planet gear carrier may result in frictional forces which slow down the rotational speed or rotational movement of the planet gears relative to each other and thus in a blocking effect, since the speed of the output cylindrical gears relative to each other is also reduced by the reduced rotational speed of the planet gears relative to each other. The locking effect can thus be obtained very effectively.

The planet gears of the at least one pair of planet gears may have conical teeth in such a way that, when the planet gears rotate relative to each other, the planet gears move in opposite directions to each other in order to enter a position in which they press against the planet carrier and thus cause a blocking effect. Thus, the locking effect can be obtained in a simple manner while the locking differential is compact.

Preferably, the output cylindrical gears have conical teeth such that, when the planet gears rotate relative to each other, the output cylindrical gears move relative to each other into a position in which they are pressed against each other and thus cause a blocking effect. Thus, the mutual pressing of the output cylindrical gears against each other causes a friction force between the output cylindrical gears, which friction force causes a torque to be transmitted from the relatively fast output cylindrical gear to the relatively slow output cylindrical gear. Therefore, the relative rotational speeds of the output cylindrical gears to each other are reduced, thereby effectively obtaining the locking effect.

Alternatively, it can also be provided that the output spur gear has a conical toothing in such a way that, when the planet gears rotate relative to one another, the output spur gear moves toward the planet carrier in order to enter a position in which it presses against the planet carrier and thus causes a blocking effect. In other words, the pressing of the respective output cylindrical gear against the planet carrier causes the rotational speed of the output cylindrical gear to be adjusted towards the rotational speed of the planet carrier. Therefore, the relative rotational speed of the output cylindrical gear is reduced and the lock-up effect is effectively obtained.

The planet carrier may have a respective defined friction area for each of said planet gears against which the respective planet gear may press (to cause a locking effect). In particular, wear caused by pressure forces or normal forces acting between the respective planet gear and the planet carrier can thus be reduced.

The respective friction area may have a structure, in particular a friction disk, for increasing the friction between the friction area and the planet gear pressed against the friction area. Therefore, the locking effect can be effectively enhanced by the increased friction and thus the increased frictional force (static frictional force or sliding frictional force). Preferably, the structure protrudes (axially) from the planet carrier. Thus, the movement distance that the respective planet gear has to travel to press against the planet carrier or the structure to achieve the blocking effect can be shortened, so that the blocking effect can be caused more quickly.

The respective friction region may have a recess in the planet gear carrier, in which recess the structure is preferably accommodated. The spur gear differential can therefore be constructed compactly.

The respective planet gears can have (radial and/or axial) projections for pressing against the planet carrier, preferably the respective friction region or the respective structure. In this way, the travel distance over which the respective planet gear has to be pushed against the planet carrier or the respective friction region/structure to achieve the blocking effect can be shortened, so that the blocking effect can be produced more quickly.

The first and/or second output cylindrical gear can each have a (further) friction region against which the respective further output cylindrical gear can be pressed (to cause a blocking effect). In particular, wear caused by the pressure forces or normal forces acting between the output spur gears can thus be reduced.

The respective (further) friction area may have a structure, in particular a friction disk, for increasing the friction between the friction area and the output spur gear, which is each pressed against the friction area. The blocking effect can thus be increased by the increased friction and thus the increased friction.

For a particularly compact construction, the respective (further) friction region can have a recess in the respective output spur gear, in which recess the construction is preferably accommodated.

Preferably, the tip circle diameter of the respective conical toothing decreases (continuously) from the first end side to the second end side of the respective conical toothing, and the root circle diameter of the respective conical toothing remains constant or increases (continuously) or decreases from the first end side to the second end side of the respective conical toothing. In other words, it is preferred that the surface of the enveloping tooth head extends from the first end side to the second end side with a conical taper or a downward inclination, wherein the surface of the enveloping tooth root extends from the first end side to the second end side with a cylindrical shape, i.e. parallel to the respective axis of rotation, or with a conical taper or a downward inclination, or with a conical expansion.

Advantageously, the corresponding conical tooth structure has a pitch angle in the range of 3 ° to 45 °. In other examples, the pitch angle may also be in the range of 5 ° to 35 °, 10 ° to 30 °, or 20 ° to 25 °.

Preferably, the respective conical toothing is formed at least by a demoulding bevel for producing at least one of the output spur gear and/or the planet gear, respectively. In other words, the demolding slopes provided for easy demolding of the respective gears may be provided simultaneously with the inclined shape for forming the conical or tapered tooth structure.

For advantageous production, the planet gears and/or the output spur gear can be produced in a molding method, in particular a press molding method. In a particularly preferred embodiment, the forming method is forging, in particular swaging. The production method is used in particular when the output spur gear is designed as the same component and/or the planetary gear is designed as the same component.

The spur gear differential may have at least two, three, four, five or six pairs of intermeshing planet gears rotatably disposed in a planet carrier. For example, the locking effect caused by the planetary gear can be added up to obtain a higher locking effect.

According to another aspect, the present invention relates to a method for manufacturing a spur gear differential as described above. The method comprises the following steps: the method comprises the steps of providing a planet carrier arranged for rotation about a differential shaft, providing a first output cylindrical gear coaxial with the differential shaft, providing a second output cylindrical gear coaxial with the differential shaft, providing at least one pair of rotatably arranged, intermeshing planet gears in the planet carrier such that the planet gears each mesh with one of the output cylindrical gears. At least one (or all) of the output cylindrical gear and/or the planet gears have a conical toothing in such a way that, when the planet gears rotate relative to one another, at least one of the output cylindrical gear and/or the planet gears is moved into a position in which a blocking effect is produced. The embodiments and advantages described above in relation to the spur gear differential apply analogously to this method.

4. Description of the preferred embodiments

The invention will be illustrated below in connection with the figures showing advantageous embodiments of the invention, which show:

figure 1 shows a schematic perspective view of one embodiment of a spur gear differential according to the present invention,

figure 2 shows a side view of the spur gear differential shown in figure 1,

fig. 3 shows a side view as shown in fig. 2, wherein a part of the planet gear carrier has been omitted in order to show, inter alia, the output cylindrical gear and the planet gears shown by way of example,

fig. 4 shows a top view of the spur gear differential shown in fig. 1 to 3, wherein the planet carrier is omitted to show the output spur gear and the planet gears shown by way of example,

figure 5 shows a perspective view of a part of the planet carrier as exemplified in figures 1 to 4,

figure 6 shows a schematic perspective view of the output cylindrical gear as exemplified in figures 1 to 4,

figure 7 shows a perspective view of the planet gear as shown in figures 1 to 4,

FIG. 8 shows a side view of the planetary gear shown in FIG. 7, together with tip, pitch and root angles.

Fig. 1 shows an exemplary spur gear differential 1 according to the invention for compensating for different rotational speeds of a driven shaft of a motor vehicle during an overbending in a known manner. The spur gear differential 1 has a planet gear carrier (or differential housing) 2 arranged for rotation about a differential axis X, which is driven by an engine, for example an internal combustion engine or an electric motor, for example via a manual transmission and a cardan shaft. For this purpose, it can be provided, for example, that a drive element is formed by the planet carrier 2 in order to transmit the engine power to the planet carrier 2 (also referred to as "final drive" or "axle drive" or "final drive"). The drive element can be designed so as to be detachable or not detachable from the planet carrier 2, for example by means of a one-piece design or a material-bonded design. For example, the planet carrier 2 is radially extended and the drive element is formed in the radial extension. The drive member is, for example, a cylindrical gear.

The spur gear differential 1 also has a first output spur gear (first sun gear) 3 arranged coaxially with respect to the differential axis X and a second output spur gear (second sun gear) 4 also arranged coaxially with respect to the differential axis X. Each

output spur gear

3,4 has a

respective bearing region

3a, 4a for rotatably supporting the respective

output spur gear

3,4 within the respective bearing region 2a of the planet gear carrier 2, so that the

output spur gear

3,4 is rotatable relative to the planet gear carrier 2 about the differential axis X. Each

support region

3a, 4a is preferably designed as a projection. Each

output spur gear

3,4 also has a respective (further)

bearing region

3b, 4b, by means of which the respective

output spur gear

3,4 is coupled in a rotationally fixed manner to a respective output shaft, not shown in detail, so that the respective output shaft is also arranged coaxially with respect to the differential axis X. The

respective bearing region

3b, 4b can be designed as a bore, in particular a through bore, in the respective

output spur gear

3, 4.

The spur gear differential 1 also has at least one planetary gear pair 5 of intermeshing planetary gears 6,7 rotatably mounted in the planetary gear carrier 2, wherein the planetary gears 6,7 each mesh with an

output spur gear

3, 4. In the embodiment of the spur gear differential 1 shown in fig. 1 to 4, the (first) planet gears 6 mesh with the first output spur gear 3, wherein the (second) planet gears 7 mesh with the second output spur gear 4. As can be seen from fig. 1 to 4, three planetary gear pairs 5 of intermeshing planetary gears 6,7 can be rotatably arranged in the planetary gear carrier 2. In other embodiments, it is also possible to provide (only) two, four, five or six planetary gear pairs 5 of intermeshing planetary gears 6, 7. A plurality of planetary gear pairs 5 of intermeshing planetary gears 6,7 are preferably evenly distributed around the differential axis X.

Each planet gear 6,7 is rotatably mounted or mounted in the planet carrier 2 about a respective axis of rotation P. The respective axes of rotation P are substantially parallel to the differential axis X. Each of the planet gears 6,7 may have a

respective bearing region

6a, 7a for supporting the respective planet gear 6,7 in a respective bearing region 2b formed in the planet carrier 2. The

respective bearing area

6a, 7a may have at least one projection which is rotatably seated or mounted in a corresponding recess of the bearing area 2b so as to be rotatably mounted about the respective axis of rotation P. The

respective bearing region

6a, 7a can also have two projections arranged on opposite sides of the respective planet gear 6,7, each projection being rotatably arranged in a corresponding recess of the bearing region 2 b.

As can be seen from fig. 1, the planet gear carrier 2 can be designed in multiple parts, in particular in two parts, in order to allow, for example, a simple assembly of the

output spur gears

3,4 and the planet gears 6, 7. In particular, the two parts of the planet carrier 2 can be designed to be substantially identical. Fig. 5 shows an example of a part of a multi-part, in particular two-part, planet carrier 2.

The invention now provides that at least one of the

output spur gears

3,4 and/or the planet gears 6,7 has a conical toothing, so that when the planet gears 6,7 rotate relative to one another, i.e. when different rotational speeds on the output shaft are produced by the spur gear differential 1, at least one of the

output spur gears

3,4 and/or the planet gears 6,7 is moved into a position in which a blocking effect is produced. In the embodiment shown in the figures, both the output cylindrical gears 3,4 and the planetary gears 6,7 have conical teeth, i.e. have a

conical tooth structure

3c,4c,6c,7 c. They can be clearly seen in particular from fig. 4, 6 and 7.

According to the embodiment shown in the figures, the latch effect is caused as follows. If the planet gears 6,7 rotate relative to each other, the

conical toothing

6c,7c causes the planet gears 6,7 to move towards the planet carrier 2, in particular in opposite directions to each other. The planet gears 6,7 are thus each moved axially along their respective rotational axis P, i.e. the

respective bearing region

6a, 7a also results in the respective planet gear 6,7 being mounted or mounted axially displaceably (with play) in the planet gear carrier 2. Looking at fig. 1 and 4, the planet gear 6 thus moves to the right, while the planet gear 7 moves to the left. By means of said movement, the planet gears 6,7 each finally enter a position in which the planet gears 6,7 are pressed against the planet carrier 2 and thus cause a blocking effect. That is, the pressing of the planet gears 6,7 against the planet carrier 2 causes a (frictional) force that decelerates the rotational speed of the planet gears 6,7 relative to each other, thereby simultaneously reducing the relative rotational speed of the output cylindrical gears 3,4 to each other and, thus, of the driven shafts that are rotationally fixedly coupled thereto.

In order to further increase the aforementioned effect, the planet carrier 2 can have, as shown in particular in fig. 1, a respective defined friction region 2c for each of the planet gears 6,7, against which the respective planet gear 6,7 can be pressed. The friction zone 2c is preferably designed to reduce wear occurring on the contact surfaces between the planet gear carrier 2 and the respective planet gears 6, 7. For this purpose, means known from friction clutches can be used, for example.

As is shown by way of example in fig. 1, the respective friction area 2c can have a friction disk 2d for increasing the friction between the friction area 2c and the planetary gears 6,7 pressed against the friction area 2 c. The friction disk 2d is preferably arranged in the friction region 2c in such a way that it protrudes (in the axial direction, i.e. in the direction of the differential axis X) from the planet carrier 2, in particular by a predetermined value, for example by 0.5 mm. However, instead of the friction plate 2d, the friction area 2c may also have any other structure for increasing the friction between the friction area 2c and the planet gears 6,7 pressed against the friction area 2c, which preferably protrude from the planet carrier 2 as described above. The friction region 2c preferably has a recess formed in the planet gear carrier 2, in which the structure or friction plate 2d is accommodated, for example. The recess preferably has a depth such that the structure received in the recess may slightly protrude from the planet carrier 2 as described above. The depth is preferably 1 mm, and therefore a 1.5 mm thick structure or friction plate projects 0.5 mm from the planet carrier 2.

As can be seen in particular from fig. 1, 4 and 7, the respective planet gears 6,7 can have (radial and/or axial)

projections

6b,7b for pressing against the planet carrier 2 or the respective friction region 2 c. As can be seen in particular in fig. 7, the

projections

6b,7b are preferably formed integrally with the

respective bearing region

6a, 7a, in particular as projections of the

respective bearing region

6a, 7a, and/or coaxially with the axis of rotation P. The areas of the

respective protrusions

6b,7b against which the planet carrier 2 or the respective friction area 2c is pressed may have a structure for increasing the friction between the planet carrier 2 or the friction area 2c and the

planet gears

6b,7b pressed against the planet carrier 2 or the friction area 2 c.

Since the

output spur gears

3,4 of the spur gear differential 1, which are shown by way of example in the figures, also have conical teeth, they are moved by their

conical tooth structures

3c,4c and the planet gears 6,7, which rotate relative to one another (also) into a position in which the locking effect is brought about. The

output spur gears

3,4 are therefore preferably mounted axially (along the differential axis X) movably relative to the planet carrier 2. Specifically, the output cylindrical gears 3,4 as shown in fig. 1 to 4 are moved relative to each other so as to finally enter a position in which the output cylindrical gears 3,4 are pressed against each other and thus cause a blocking effect. This mutual abutment thus results in a force which, by means of the frictional force thus increasing between the output cylindrical gears 3,4, reduces the rotational speed of the output cylindrical gears 3,4 relative to one another and thus of the driven shafts rotationally fixedly coupled thereto, the torque thus being transmitted (directly) from the faster output cylindrical gear to the slower output cylindrical gear.

In order to increase the aforementioned locking effect achieved by means of the output cylindrical gears 3,4, the first and/or second

output cylindrical gear

3,4 may each have a (further) friction region against which the respective further

output cylindrical gear

3,4 can be pressed. The friction region is preferably arranged on a surface of the respective

output spur gear

3,4 which is opposite the respective other

output spur gear

3, 4. The (further) friction zone may in particular be formed according to the friction zone 2c described above. The (further) friction area may thus have, for example, a structure, in particular a friction disk, for increasing the friction between the friction area and the

output spur gear

3,4, which is pressed against the friction area in each case. Such friction areas have, for example, recesses which are formed in the respective

output spur gears

3,4 and in which the structure, i.e. for example the friction disks, are preferably accommodated.

As an alternative to the conical-toothed structure of the output cylindrical gears 3,4, as described above, in which the output cylindrical gears 3,4 are moved relative to one another by the planet gears 6,7 rotating relative to one another, the output cylindrical gears 3,4 can also have conical teeth, so that they are moved toward the planet carrier 2 as a result of the rotation of the planet gears 6,7 relative to one another into a position in which the output cylindrical gears 3,4 are pressed against the planet carrier 2 and thus cause a blocking effect. In other words, the direction of movement of the output cylindrical gears 3,4 which are used in the preferred embodiment and are to be moved relative to one another can be reversed by a corresponding design of the

conical toothing

3c,4c and a changed engagement between the output cylindrical gears 3,4 and the respective planet gears 6, 7. The same applies to the planet gears 6, 7.

The invention is not limited to the preferred embodiment described above of the blocking effect caused not only by the

output spur gears

3,4 but also by the planetary gears 6, 7. The locking effect can also be achieved, for example, only by the above-described design of the

output spur gears

3, 4. Alternatively, the blocking effect can also be achieved solely by the above-described design of the planet gears 6, 7. It is also not necessary for the two output cylindrical gears 3,4 or the two planet gears 6,7 to have conical teeth. For example, it can also be provided that only one of the

output spur gears

3,4 or only one of the planet gears 6,7 has conical teeth in order to produce the blocking effect according to the invention by the movement of the

output spur gear

3,4 or the planet gear 6, 7.

The respective gear with conical toothing is thus, for example, one or both of the output cylindrical gears 3,4 and/or one or both of the planetary gears 6,7 (compare in particular fig. 6 and 7), which is used in the cylindrical gear differential 1 just like a corresponding cylindrical gear, except that it has the gear shape of a bevel gear. As can be seen clearly in fig. 8 with regard to one planetary gear 6,7, for example, the tip circle diameter of the respective

conical toothing

6c,7c decreases (continuously) from the first end side of the respective

conical toothing

6c,7c to the second end side of the

conical toothing

6c,7c provided, for example, on the

projection

6b,7b, and the root circle diameter of the respective

conical toothing

6c,7c also decreases from the first end side to the second end side of the respective conical toothing. Alternatively, however, it can also be provided that the root circle diameter of the respective

conical toothing

6c,7c remains constant or increases from the first end side to the second end side of the respective conical toothing. In other words, the respective gearwheel has a substantially cylindrical running surface, just like a cylindrical gearwheel, wherein the profile of the tooth structure (continuously and monotonically) changes in a conical or conical manner from one end side of the tooth structure to the other end side of the tooth structure. The respective gear wheel with the conical tooth structure therefore also has a pitch angle. As can be seen, for example, from fig. 4, the taper of the conical toothing, i.e. the design of the conical toothing or the taper for forming the respective gearwheel, is preferably oriented in a direction which corresponds to the direction of movement of the respective gearwheel into the position for achieving the blocking effect.

As can be clearly seen from fig. 8, it is preferred that the rays of the tip angle, the pitch angle and the root angle of the respective conical tooth structures intersect at a point of intersection, for example on the axis of rotation P. Preferably, the tip, pitch and root angles are all (slightly) different, but always extend in one direction. The pitch angle may be, for example, in the range of 3 ° to 45 °. In other examples, the pitch angle is in a range of 5 ° to 35 °, 10 ° to 30 °, or 20 ° to 25 °. The tip angle is particularly preferably 3 ° or 5 °. The root angle is particularly preferably 5 ° or 3 °. Preferably, the conical tooth structure (seen in a top view of the respective tooth) is straight or helical, i.e. in particular parallel or inclined with respect to the respective axis of rotation P (seen in a top view of the respective tooth). The tooth structure type of the tooth structure is, for example, an involute tooth structure (see, for example, fig. 3).

A particular advantage of the conical toothing of the respective gearwheel lies in the fact that it is simple to manufacture such a gearwheel. The gear to be produced can thus be more easily ejected from the respective mold for producing the respective gear because of the taper made or formed in the production process, i.e. in particular the oblique tooth structure provided by the taper, which is advantageous in particular in the case in which the respective gear is not of the helical tooth type. The respective conical tooth structure can thus be formed at least by the demolding bevel for producing the respective gear. The demolding bevel is therefore advantageous, in particular, for the reason that the component, i.e. here the gear, will get stuck elsewhere in the respective mold for producing the component. In particular, a shaping method, such as, for example, a press-forming method, is suitable for producing the planetary gears 6,7 and/or the output cylindrical gears 3,4, in particular gears having conical teeth. It is particularly preferred that the forming method is forging, especially swaging. Steel is used as the preferred material for making the gears. The respective gear or its material, i.e. in particular steel, can be hardened and/or tempered.

The invention is not limited to the embodiments shown. All the aforementioned features or the features shown in the figures, i.e. in particular the features of the

output spur gears

3,4 and of the planet gears 6,7, can advantageously be combined with one another in any desired manner within the scope of the invention.

Claims

1. A spur gear differential (1), the spur gear differential (1) having:

-a planet carrier (2) arranged for rotation about a differential axis (X),

-a first output cylindrical gear (3), said first output cylindrical gear (3) being coaxially arranged with respect to said differential shaft (X),

-a second output cylindrical gear (4), said second output cylindrical gear (4) also being coaxially arranged with respect to said differential shaft (X), and

-at least one pair (5) of intermeshing planet gears (6,7) rotatably arranged in the planet carrier (2), wherein the planet gears (6,7) each mesh with one output cylindrical gear (3,4),

wherein at least one of the output cylindrical gear (3,4) and/or the planetary gear (6,7) has a conical toothing such that when the planetary gears (6,7) are rotated relative to each other, the at least one of the output cylindrical gear (3,4) and/or the planetary gear (6,7) is moved into a position causing a blocking effect.

2. The cylindrical gear differential (1) according to claim 1, wherein the planet gears (6,7) of the at least one pair (5) of planet gears (6,7) have conical teeth, such that when the planet gears (6,7) rotate relative to each other, the planet gears (6,7) move towards the planet carrier (2) so as to enter a position in which the planet gears (6,7) press against the planet carrier (2) and thus cause a blocking effect.

3. The cylindrical gear differential (1) according to claim 2, wherein the planet gears of the at least one pair (5) of planet gears (6,7) have conical teeth, such that when the planet gears (6,7) rotate relative to each other, the planet gears (6,7) move in opposite directions to each other in order to enter a position in which the planet gears (6,7) are pressed against the planet gear carrier (2) and thus cause a blocking effect.

4. The spur gear differential (1) according to any one of the preceding claims, wherein the output spur gears (3,4) have conical teeth, such that when the planet gears (6,7) rotate relative to each other, the output spur gears (3,4) move relative to each other into a position in which the output spur gears (3,4) are pressed against each other and thus cause a locking effect.

5. The cylindrical gear differential (1) according to any one of claims 1 to 3, wherein the output cylindrical gears (3,4) have bevel gears such that when the planet gears (6,7) rotate relative to each other, the output cylindrical gears (3,4) move towards the planet carrier (2) into a position in which the output cylindrical gears (3,4) press against the planet carrier (2) and thus cause a locking effect.

6. The spur gear differential (1) according to any one of the preceding claims, wherein the planet carrier (2) has a respective defined friction area (2c) for each planet gear (6,7), against which the respective planet gear (6,7) can be pressed.

7. The spur gear differential (1) according to claim 6, wherein the respective friction area (2c) has a structure, in particular a friction plate (2d), for increasing the friction between the friction area (2c) and the planet gears (6,7) pressed against the friction area (2c), wherein the structure (2c) preferably protrudes (in the axial direction) from the planet carrier (2).

8. Cylindrical gear differential (1) according to claim 6 or 7, wherein the respective friction zone (2c) has a recess in the planet carrier (2), said structure (2c) preferably being accommodated in said recess.

9. The spur gear differential (1) according to any one of the preceding claims, wherein the respective planet gear (6,7) has a (radial and/or axial) projection (6b,7b) for pressing against the planet carrier (2), preferably against the respective friction zone (2 c).

10. The spur gear differential (1) according to any one of the preceding claims, wherein the first output spur gear (3) and/or the second output spur gear (4) each have a (further) friction area against which the respective further output spur gear (3,4) can be pressed.

11. The spur gear differential (1) according to claim 10, wherein the respective (further) friction area has a structure, in particular a friction plate, for increasing the friction between the friction area and the output spur gear wheels (3,4) respectively pressed against the friction area.

12. Spur gear differential (1) according to claim 10 or 11, wherein the respective (further) friction area has a recess in the respective output spur gear (3,4), in which recess the structure is preferably accommodated.

13. The spur gear differential (1) according to any one of the preceding claims, wherein the tip circle diameter of the respective conical tooth structure (3c,4c,6c,7c) decreases from the first end side to the second end side of the respective conical tooth structure (3c,4c,6c,7c), and wherein the root circle diameter of the respective conical tooth structure (3c,4c,6c,7c) remains constant or increases or decreases from the first end side to the second end side of the respective conical tooth structure (3c,4c,6c,7 c).

14. A spur gear differential (1) according to any of the preceding claims, wherein the respective conical tooth structure (3c,4c,6c,7c) has a pitch angle in the range of 3 ° to 45 °, preferably 5 ° to 35 °, particularly preferably 10 ° to 30 °, for example 20 ° to 25 °.

15. The spur gear differential (1) according to any one of the preceding claims, wherein the respective conical tooth structure (3c,4c,6c,7c) is constituted at least by a demoulding bevel for manufacturing the respective at least one of the output spur gear (3,4) and/or the planet gear (6, 7).

16. The spur gear differential (1) according to one of the preceding claims, wherein the planet gears (6,7) and/or the output spur gear (3,4) are produced in a forming method, in particular a press-forming method.

17. The spur gear differential (1) according to claim 16, wherein the forming method is forging, in particular swaging.

18. Cylindrical gear differential (1) according to one of the preceding claims, the cylindrical gear differential (1) having at least two (5), three (5), four (5), five (5) or six (5) pairs of intermeshing planet gears (6,7) rotatably arranged in the planet carrier (2).

19. Method of manufacturing a spur gear differential (1) according to any of the preceding claims, having the steps of:

-providing a planet carrier (2) arranged for rotation about a differential axis (X),

-providing a first output cylindrical gear (3) coaxial with the differential shaft (X),

-providing a second output cylindrical gear (4) coaxial with the differential shaft (X),

-providing at least one pair (5) of mutually engaging planet gears (6,7) rotatably arranged in the planet carrier (2) such that the planet gears (6,7) each engage with one output cylindrical gear (3,4),

wherein at least one of the output cylindrical gear (3,4) and/or the planetary gear (6,7) has a conical toothing, such that when the planetary gears (6,7) rotate relative to each other, the at least one of the output cylindrical gear (3,4) and/or the planetary gear (6,7) moves into a position causing a blocking effect.